CN108027622A

CN108027622A - For adjusting the method for adjustment unit and there is the consumption measuring device of this adjustment unit

Info

Publication number: CN108027622A
Application number: CN201680037331.XA
Authority: CN
Inventors: G·里克特内格; V·布拉泽尔; M·巴克纳; O·J·周
Original assignee: AVL List GmbH
Current assignee: AVL List GmbH
Priority date: 2015-06-23
Filing date: 2016-06-09
Publication date: 2018-05-11
Also published as: AT517215A4; US20180275697A1; WO2016206983A3; EP3314348A2; AT517215B1; KR20180020153A; JP2018520436A; WO2016206983A2

Abstract

The present invention relates to a kind of adjustment unit (3), the adjustment unit carries matrix (20) and buffer (21), wherein medium is conducted through described matrix (20) and the thermostat units (23) with the first heating surface (24) and the second heating surface (25) is disposed between matrix (20) and buffer (21), and the temperature span between first heating surface (24) and second heating surface (25) is adjusted by the thermostat units (23).Adjustment unit (3) is adjusted to maintain the theoretical temperatures (T provided in advance of the medium_soll), wherein, regulated variable (Y) for adjusting the adjustment unit (3) is made of model part (A) and adjusting part (R), which calculates in order to medium progress temperature adjustment and in power (P needed for adjustment unit (3)_v), the power (P which is calculated with the model part (A)_v), wherein, by theoretical temperatures (T_soll) and actual temperature (T_ist) the adjusting error (F) that forms is included in the adjusting partly in (R) exponentially.

Description

Method for adjusting an adjusting unit and consumption measuring device having such an adjusting unit

The invention relates to a method for controlling a control unit having a main body through which a medium is guided and a buffer reservoir, and a temperature control unit having a first heating surface and a second heating surface is arranged between the buffer reservoir and the main body, and by means of which a temperature span between the first heating surface and the second heating surface is controlled, and to the use of the method in a consumption measuring device for measuring the consumption of a gaseous medium. The invention further relates to a consumption measuring device for measuring the consumption of a gaseous medium, having an inlet connection, at which the gaseous medium is fed to the consumption measuring device, and having an outlet connection, at which the gaseous medium is supplied by the consumption measuring device, wherein a gas path is provided between the inlet connection and the outlet connection, a consumption sensor is arranged in the gas path, and an adjusting unit for adjusting the temperature of the gaseous medium is arranged in front of the consumption sensor, and a pressure adjusting unit, in which the gaseous medium is depressurized, is arranged between the adjusting unit and the consumption sensor.

In order to accurately measure the fuel consumption of an internal combustion engine on a test bench, accurate regulation of the temperature and pressure of the fuel fed to the internal combustion engine is necessary. In this case, the fuel consumption is often measured by means of a known Coriolis (Coriolis) flow sensor. In this case, it is often the case for the liquid fuel that a pre-circuit and a metering circuit are provided, in which the liquid fuel is circulated. A flow sensor is arranged between the pre-circuit and the measuring circuit. The measuring circuit is closed via the internal combustion engine to be supplied. The purge quantity, which is usual for liquid fuel supply systems, is thus fed back into the measuring circuit. The pre-circuit is used to feed the quantity of fuel consumed in the internal combustion engine to the measuring circuit. Thereby, the flow sensor disposed therebetween can accurately measure the amount of consumed liquid fuel. Since liquid fuels have a significant coefficient of thermal expansion, the temperature in the measuring circuit must be kept as constant as possible in order to prevent possible measuring errors due to volume changes caused by temperature fluctuations of the fuel in the measuring circuit. After the purge quantity fed back to the measuring circuit is heated by the fuel supply system of the internal combustion engine, a temperature regulation of the fuel in the inlet to the internal combustion engine is necessary. Even in the case of a pilot circuit, volume changes due to temperature fluctuations should be avoided for precise consumption measurements. The fuel in the pre-circuit is therefore also tempered. Furthermore, the pressure of the liquid fuel fed to the internal combustion engine is also regulated as constant as possible by means of the pressure regulating unit. Furthermore, the temperature as well as the pressure of the fuel are related to the current flow rate. Examples of such measurements of fuel consumption, based on adjustments to liquid fuel, can be found in US 2014/0123742A1 and EP 1 729 100A1. The temperature of the fuel is regulated by means of a cooling liquid via a heat exchanger. However, such heat exchangers are sluggish and only allow slow temperature changes, but this is not sufficient for liquid fuels, since the temperature must only be kept as constant as possible. In addition, such heat exchangers require controls and additional components for the operation of the heat exchanger, which also makes the apparatus more expensive.

The system described above for measuring the fuel consumption of an internal combustion engine can in principle also be used in gaseous fuels, for example for gas engines. However, such a system is disadvantageous for gaseous fuels, since corresponding compressors or fans for circulating the gaseous fuel in the pre-circuit and the measuring circuit are required, which would make the system significantly more expensive and enlarge it. In addition, the compressor can greatly influence the temperature of the gaseous medium, which is counter-productive for temperature regulation purposes.

For gaseous fuels like natural gas or hydrogen, the additional problem arises that the gaseous fuel is usually present or supplied at a high pressure and therefore, for use as fuel in an internal combustion engine (here a gas engine), the pressure must first be reduced to the required lower pressure. However, when the gaseous fuel is reduced in pressure, the fuel cools down strongly (joule-thomson effect), which is problematic for subsequent components of the conditioning apparatus, for example due to the generation of condensate and icing of the gas lines or other components in the gas lines. Therefore, the gaseous fuel is typically heated prior to reducing the pressure to produce the desired fuel temperature by reducing the pressure. The temperature after depressurization may vary strongly due to pressure fluctuations of the fed gaseous fuel and due to the correlation of the temperature after depressurization with the composition of the gaseous fuel. For such strongly varying temperatures at the inlet, the systems described in US 2014/0123742A1 or EP 1 729 A1 are not suitable. The dull heat exchangers described in these documents generally do not compensate for strong temperature fluctuations.

The heat exchanger is slow and allows only slow temperature changes. This adjustment by means of a heat exchanger is therefore unsuitable for heavy load changes.

This results in the current prior art that must remain stable for a period of time after such load changes. During this time, the temperature is unstable and a high accuracy measurement is not possible for the flow sensor. For operation independent of input temperature variations, the power density of the heat exchanger must be increased. However, this is not technically as well achievable and requires redesign of the heat exchanger if possible. For a constant power density, a much larger space requirement arises. Another possibility may be a more aggressive regulation characteristic of the heat exchanger. However, the device is not limited to the specific type of the deviceThis in turn means a larger overshootAnd undershoot (Unterschwingen) and the associated poorer dynamics in terms of possible theoretical temperature changes. However, enlarging the heat exchanger is only helpful in the case of liquids. In the case of gaseous media, the flow changes directly result in pressure changes and theoretical temperature changes. The heat exchanger must therefore make possible exceptionally fast theoretical temperature changes, which, however, is not practically possible with heat exchangers which are operated with cooling liquid. For this reason, the power available for a constant quality must be further increased, in which case merely increasing the power is not useful. An alternative solution would leave the regulator regulating the heat exchanger more aggressively, but this would cause more overshoot and undershoot. Thus, accurate and rapid temperature adjustment is impossible.

In the case of gaseous media, however, changes in flow directly result in changes in pressure and theoretical temperature. The heat exchanger must therefore make possible exceptionally fast theoretical temperature changes, which, however, is not practically possible with heat exchangers which are operated with cooling liquid. In addition, the power increase is of little use in terms of dynamics, since only the power density is decisive for the change in the theoretical value, not the absolute power. Precise and rapid temperature regulation with the aid of heat exchangers is not possible in the event of strong flow fluctuations. This applies both to gaseous and liquid media to be conditioned.

A first object of the invention is therefore to provide a method for regulating a regulating unit of the type mentioned above, by means of which the temperature of a gaseous or liquid medium can be precisely regulated and kept constant despite large fluctuations in the flow rate or pressure of the medium.

This object is achieved by a method in which an adjustment unit is adjusted to maintain a predetermined setpoint temperature of the gaseous medium, wherein an adjustment variable for adjusting the adjustment unit is formed by a model part, which calculates the power required for preheating the gaseous medium in the adjustment unit, and an adjustment part, which corrects the power calculated with the model part, wherein an adjustment error formed from the setpoint temperature and the actual temperature is exponentially calculated into the adjustment part. The power required for tempering the gaseous medium can be roughly calculated by the model part. The adjustment part that corrects the model part is then used for fine adjustment. By an exponential consideration of the adjustment error in the adjustment portion, the heat propagation in the adjustment unit can be approximated, whereby the adjustment unit can be adjusted particularly precisely.

In this case, the control unit is preferably embodied according to the invention as a base body, in which a medium line through which the gaseous medium flows is arranged, and a buffer reservoir for storing heat, wherein a temperature control unit is arranged between the base body and the buffer reservoir. By means of the regulating unit, rapid regulating interventions can be achieved, which are necessary for a rapid, precise and stable temperature regulation in the regulating unit.

In a gas engine, the flow rate of gaseous fuel is also strongly correlated with the load of the gas engine. This in turn means that the heat exchanger in US 2014/0123742A1 or EP 1 729 A1 must be able to avoid such strongly fluctuating flows in order to temper the gaseous fuel in the pre-circuit and in the measurement circuit. The generally described dull heat exchangers are not suitable for this or have to be dimensioned correspondingly, which, however, makes them more complex and more expensive.

In addition, the temperature control of the gaseous fuel with such heat exchangers is also imprecise, and in particular a meaningful supercooling (superheating or supercooling) as a function of the flow rate or pressure must be taken into account.

Furthermore, conventional plants for liquid fuels are usually only capable of withstanding pressures of up to 10 bar. For gaseous fuels, a compressive strength of up to 300 bar is required for preheating. This immediately excludes the usual equipment for most applications with gaseous fuels.

The known devices for accurately measuring the consumption of liquid fuel by an internal combustion engine are therefore not suitable for gaseous fuels or are only conditionally suitable for gaseous fuels. Therefore, gaseous fuels require other ways to be able to measure the consumption of gaseous fuels accurately and at a reasonable cost.

Gas pressure regulating devices in natural gas networks are known to depressurize high transport pressures to the required consumption pressure, in which devices gas quantity measuring devices may also be integrated.

Such gas pressure regulating devices usually comprise an input-side natural gas preheater, often in the form of a water heating bath, through which natural gas is conducted in a pipeline, or in the form of a water/natural gas heat exchanger. With the natural gas preheater, the natural gas is heated before being depressurized to consumption pressure to compensate for the cooling due to the joule-thomson effect. However, such gas pressure regulating devices may have high requirements on the accuracy of the output pressure, as well as special requirements on the output temperature. The effect of the flow rate also changing slowly with time is negligible in such a gas pressure regulating device. In such a gas pressure regulating device, rapid, sudden flow changes do not occur anyway.

The thermal power required for gas preheating of the supplied gaseous fuel to reach the desired temperature after depressurization can be calculated according to known formulas and used in such gas pressure regulating devices to regulate the natural gas preheater. This formula can also be used for tempering gaseous fuels in the tempering of the heat exchanger. However, sufficient control accuracy can only be achieved in this way for relatively slow flow rate changes. For a gas pressure regulating device with only a very small and only slowly changing flow rate, this is extended. The achievable accuracy of the temperature regulation in this known manner is not sufficient in applications in which the flow rate changes highly dynamically (in the sense of rapid and strong flow rate changes), for example in the measurement of the consumption of an internal combustion engine (for example an internal combustion engine or a gas turbine).

A similar problem with accurate measurement of consumption typically occurs in the following cases: the consumer is operated by feeding the gaseous medium to the consumer, wherein the gaseous medium is at a pressure higher than or is conveyed at a consumption pressure in the consumer. Other examples than internal combustion engines, which impose similar accuracy requirements, are fuel cells supplied with hydrogen, rocket engines or jet engines.

In this case, the pressure of the gaseous medium can be adjusted relatively easily by means of a conventional pressure adjustment device. On the contrary, the regulation of the medium temperature is significantly more difficult to achieve due to the aforementioned problems.

A further object of the present invention is therefore to provide a method for measuring the consumption of gaseous fuel by a consumer, which method allows the gaseous fuel at the outlet to have a temperature which is as constant as possible despite a highly dynamically fluctuating flow rate and/or pressure.

According to the invention, this object is achieved in that: the gaseous medium flows along a gas path through a consumption measuring device, wherein the consumption is measured by a consumption sensor, and the gaseous medium is tempered by an adjusting unit before the consumption sensor, and the gaseous medium between the adjusting unit and the consumption sensor is depressurized, and the adjusting unit is adjusted according to the adjusting method of the invention.

Further preferred and advantageous designs of the method and the adjustment unit are given by the independent claims and the description of the invention.

The invention will be explained in more detail hereinafter with reference to fig. 1 to 5, which fig. 1 to 5 show by way of example, schematically and without limitation, various designs in which the invention is advantageous. Shown here are:

FIG. 1 is a circuit diagram of a consumption measuring apparatus according to the present invention,

figure 2 is a consumption measuring device in an alternative design,

figure 3 is a view of the adjustment unit,

FIG. 4 is a regulating unit with active cooling in a buffer store, an

Fig. 5 is a preferred design of the consumption measuring device.

As shown in FIG. 1, the invention proceeds from a consumption measuring device of similar design, for example from gas pressureAs is known in force adjustment devices. The consumption measuring device 1 receives the gaseous medium from the medium supply device 2. The medium supply 2 can be, for example, a gas line or a medium container, for example, a gas cartridge. The gaseous medium is usually supplied from the medium supply 2 at a non-constant supply pressure p _e Is taken and flows through the consumption measuring device 1 along the gas path 17. Here, the pressure p is input _e Pressures of up to 300 bar and higher are possible. The obtained gaseous medium is fed in a gas path 17 to a conditioning unit 3, in which conditioning unit 3 the gaseous medium is heated to a certain temperature T ₁ . The heated gaseous medium is then fed to a pressure regulating unit 4, in which pressure regulating unit 4 the gaseous medium is depressurized to a reduced pressure p _red . By reducing the pressure in the pressure regulating unit 4, the temperature of the gaseous medium becomes the reduced pressure temperature T _red . In the case of natural gas as the gaseous medium, the gaseous medium is cooled by the joule-thomson effect. In the case of hydrogen, even an increase in the temperature of the gaseous medium can result from the depressurization. After depressurization in the pressure regulating unit 4, the gaseous medium is fed to a consumption sensor 5, for example a mass flow sensor or a flow sensor, for example in the form of a known coriolis sensor. Gaseous medium at output pressure p _a And an output temperature T _a Leaves the consumption measuring device 1 and feeds consumers 6, such as internal combustion engines, gas turbines or fuel cells. The amount of gaseous medium consumed by the consumer 6 is thus measured by the consumption sensor 5. For accurate measurements, high temperature stability and pressure stability are necessary.

In the embodiment according to fig. 1, the output pressure p _a And an output temperature T _a Substantially corresponding to the reduced pressure p after the pressure regulating unit 4 _red And the decompression temperature T _red . In an alternative embodiment, the depressurization can also be carried out in two stages (or else in a plurality of stages), as is illustrated in accordance with fig. 2. The gaseous medium located upstream of the consumption sensor 5 is brought to a reduced pressure p _red And the decompression temperature T _red By means of which the consumption is measured.Downstream of the consumption sensor 5 in the flow direction, a second pressure control unit 7 is arranged, which depressurizes the gaseous medium to an output pressure p _a From which the output temperature T is also derived _a . A certain consumption sensor 5, for example a coriolis sensor, is preferably used with a high accuracy at high pressures and therefore high densities of the gaseous medium. It is therefore advantageous first only to depressurize to a pressure which yields a sufficiently high measurement accuracy, and then to depressurize to a lower required output pressure p _a 。

For an accurate consumption measurement of the gaseous medium through the consumer 6, the output pressure p _a And output temperature T _a Should be kept as constant as possible. But with an output pressure p _a And an output temperature T _a With input pressure and input temperature T _e The composition of the gaseous medium obtained (due to the joule-thomson effect) and the flow rate are strongly correlated, the flow rate also varying strongly in amplitude over time. In order to be able to adjust these influences, on the one hand, the output pressure p is required _a And in particular a highly dynamic temperature regulation of the regulating unit 3.

Output pressure p _a Can be carried out with sufficient accuracy by means of a conventional pressure regulating unit 4,7, for example in the form of an adjustable pressure regulating valve. Thus, the output pressure p _a Preferably in the pressure regulating circuit of the upper stage. For this purpose, a pressure sensor 8 can be provided at the outlet of the consumption measuring device 1, which pressure sensor detects the output pressure p _a And feeds a regulating unit 10, preferably in digital form.

The control unit 10 controls the first pressure control unit 4 (fig. 1) or the first and/or second pressure control unit 4,7 (fig. 2) in order to set a desired or predetermined output pressure p _a . In the exemplary embodiment according to fig. 2, the first pressure regulating unit 4 is, for example, regulated to a constant decompression pressure p _red And output a pressure p _a The regulation is performed only via the second pressure regulating unit 7.

With regard to the adjustment of the temperature, it is,the output temperature T can be determined by means of the temperature sensor 9 _a And the output temperature T is measured _a Is fed to a regulating unit 10, preferably in digital form. It is worth noting here that the temperature T is output in the following text _a The invention is described, but in principle the temperature at every arbitrary location of the consumption measuring device 1 can be used. In particular instead of the output temperature T _a The reduced pressure temperature T can be used in the same manner _red Temperature T after the regulating unit 3 ₁ Or the temperature T in the consumption sensor 5 _s . The regulating unit 10 regulates the temperature (e.g. output temperature T) from the measured temperature _a Temperature T after the regulating unit 3 ₁ Reduced pressure temperature T _red Or the temperature T in the consumption sensor 5 _s ) A manipulated variable Y for the actuating unit 3 is calculated, by means of which the actuating unit 3 can be controlled. In this connection, the current flow measured by the consumption sensor 5 can also be usedIs fed to the adjusting unit 10.

Thereby, according to the current flowAnd also adjusts the desired output temperature Ta in dependence on the adjustment of the adjustment unit 3 by the current output pressure pa. For flow fluctuating at high dynamicIn the case of which an accurate temperature regulation of the output temperature Ta is possible, a special regulating unit 3 is provided, which regulating unit 3 is combined with a special regulating method.

As shown very simply in fig. 3, the control unit 3 is embodied with a base body 20 through which a medium line 22 is guided, through which the gaseous medium to be controlled flows. A temperature control unit 23 is arranged on the base body 20, where a buffer reservoir 21 for storing heat is arranged.

The substrate 20 is not directly adjacent to the buffer reservoir 21, but is thermally insulated therefrom by the temperature control unit 23. The buffer store 21 is preferably embodied as a cooling body with a certain storage capacity. The heat sink is thus not designed with a maximum heat dissipation capacity (as is usual per se for heat sinks), but rather the heat sink should store a certain portion of the heat to be dissipated for at least a certain period of time. The temperature control unit 23 serves to control the temperature of the substrate 20 and thus of the medium flowing through.

In this case, the temperature control unit 23 is able to heat and cool the substrate 20.

The temperature control unit 23 is advantageously embodied as at least one thermoelectric module (peltier element), preferably several thermoelectric modules. Thermoelectric modules are known as semiconductor elements which are arranged between a first heating surface 24 and a second heating surface 25. Depending on the polarity of the supply voltage to be fed to the semiconductor element, either the first heating surface 24 is hotter than the second heating surface 25 or the second heating surface is hotter than the first heating surface. The thermoelectric module can thus be used to heat and cool the substrate 20 depending on the polarity of the supply voltage. This is not further explained after the structure and function of such thermoelectric modules are sufficiently known and commercially available at various power levels.

If a supply voltage is supplied to the thermoelectric module, one of the heating surfaces 24, 25 of the thermoelectric module cools down in a known manner, while the heating surface opposite this heats up. The maximum temperature span between the two heating surfaces 24, 25 depends on the operating temperature of the thermoelectric module (i.e., the temperature at the hotter heating surface). The higher the operating temperature, the higher the maximum temperature span that can be achieved between the cold and the hot heating surface. In this way, temperatures of up to 200 ℃ can be reached at the hot heating surface by means of the available thermoelectric modules, wherein the cold heating surface does not exceed 100 ℃. By simply reversing the polarity of the supply voltage, it is possible to switch quickly between cooling and heating. After the gaseous medium flowing through the conditioning unit 3 has been tempered, heating means that the heating surface 24 lying against the substrate 20 is hotter than the heating surface 25 lying opposite it. Cooling means that the heating surface 25 is a hotter heating surface and the heating surface 24 next to the substrate is a cooler heating surface.

In order to regulate the temperature of the gaseous medium, it is not necessarily necessary to change the polarity of the supply voltage when the temperature of the gaseous medium is to be lowered or raised. For this purpose, it is also possible to use the temperature span between the heating surfaces 24, 25. As a result, smaller control interventions can be made via the temperature span, and preferably larger control interventions can be made by polarity reversal of the supply voltage of the thermoelectric module.

The regulation over the temperature span is supported by the buffer store 21 acting as a heat accumulator during heating operation, i.e. when the medium is heated in the medium feed 22. With a constant supply voltage of the thermoelectric module, a stable temperature span is present at the thermoelectric module. As soon as less thermal energy or heat is now required for tempering the medium, the supply voltage at the thermoelectric module is reduced, as a result of which the temperature span also becomes smaller. This reduces the temperature at the heating surface 24 of the thermoelectric module, which is in close contact with the substrate 20. At the same time, the temperature at the opposite heating surface 25 rises. As a result, a temperature gradient is produced between the heating surface 25 and the buffer store 21 in contact therewith, as a result of which heat flows into the buffer store 21 (due to the heat flow)Expressed), and is not immediately emitted to the environment here due to the stored heat, but rather buffered (at least for a limited time). When more thermal energy is needed to temper the medium, this buffered heat is provided as support for tempering. In this case, the supply voltage is increased again, as a result of which the temperature span at the thermoelectric module is increased again. This reduces the temperature at the heating surface 25 in close contact with the buffer reservoir 21 relative to the temperature of the buffer reservoir 21. This produces a temperature gradient which in turn causes the thermal energy stored in the buffer reservoir 21 to flow into the substrate 20 (due to the heat flow)Represented by (c) and thus support the thermoelectric module while tempering the media. Thereby, canVery fast and precise reaction to rapid load changes or temperature changes and typical over-attemperation can be further avoided. For this purpose, it is advantageous to adapt the stored heat quantity of the buffer store 21 to the stored heat quantity of the substrate 20 and the medium lines 6 arranged therein, in order to make optimum use of this effect.

Although the regulating unit 3 has been described above as a temperature-regulating unit 23 in terms of a thermoelectric module, other designs of the temperature-regulating unit 23 are of course also conceivable. The temperature control unit 23 only has to be able to change the temperature span between the heating surfaces 24, 25. Physically, the thermoelectric module operates in a manner corresponding to a heat pump that receives thermal energy from an area having a lower temperature and transfers the thermal energy to a system to be heated having a higher temperature. The reversal of the polarity of the supply voltage corresponds to the setting of two heat pumps operating in opposition. Thus, in principle every device that can be classified as a heat pump concept can be used as a tempering unit 23.

In order to also be able to exploit this advantage of the adjusting unit 3 from the adjustment technology (which is a prerequisite for a fast and precise adjustment), provision can be made according to the invention for: during the adjustment, the heat flow between the buffer store 21 and the substrate 20 through which the medium flows is taken into accountFor this purpose, a regulator is provided which has a theoretical temperature default T _soll The manipulated variable Y for the adjustment unit 3 is calculated. The regulating unit 3 is controlled by means of a regulating variable Y and serves for a stable and constant temperature of the medium.

The manipulated variable Y consists of a model part a and a manipulated part R, i.e. Y = a + R. The model part a models the regulating unit 3 and serves to optimally calculate the energy or power P required for the temperature control of the medium in the regulating unit 3 _v And converted into a manipulated variable for adjustment. In order to reach the theoretical temperature T after depressurization _soll Power P required for tempering the gaseous medium _G Can be calculated according to known formulaic relationships.

Wherein T is _hot ＝T _soll +Δp _G ·μ _JT

Without Joule-Thomson effect, power P _G To the power required for tempering (heating or cooling) the medium. The current flow rateMeasured by the consumption sensor 5 and made available for use. Specific heat capacity H of the medium _G Is constant and known. Input temperature T _e May be measured by means of a suitable temperature sensor 11, for example a PT100 sensor. Pressure difference Δ p _G Representing the slave input pressure p _e To reduced pressure p _red (both of which are measurable by the pressure sensors 8, 12) pressure drop, i.e. Δ p _G ＝(p _e -p _red ). In the embodiment according to fig. 2, the reduced pressure p _red May also be known. By mu _JΤ To represent the joule-thomson coefficient of the gaseous medium. For liquid media, the joule-thomson coefficient is set to zero.

Optionally, the loss power P can also be taken into account in the adjustment unit 3 _L . For very precise and rapid regulation, this loss power P should be taken into account _L . Loss power P _L Can be modeled, for example, to adjust the ambient temperature T of the unit 3 _amb Heat emitted to the environment. Ambient temperature T _amb Which in turn can be measured by means of a suitable temperature sensor 13, for example a PT100 sensor. Using an empirical constant k obtained from a specific embodiment of the control unit 3 and known as a precondition _PL The loss power P can be calculated according to the following formula _L ：

The power P required for the temperature control in the control unit 3 is then _V From P _v ＝P _G [+P _L ]To obtain that the power canUsed as model part a. In order to determine therefrom an easily processable manipulated variable for the regulation, the required power P _V And also with the maximum available power P in the regulating unit 3 _V,MAX I.e. the model partIt is relevant.

When switching between heating and cooling is also possible in the adjustment unit 3, the model part a is thus a parameter in the range 0,1 or-1, 1.

In the specific design of the regulating unit 3 with a thermoelectric module as a temperature regulating unit 23, the required power P _V Is also converted into a supply voltage U supplied to the thermoelectric module _V . By means of the ohmic resistance R of the thermoelectric modules in the regulating unit 3 _CU From known relationsCalculate the supply voltage U _v . Similarly to the above, the model section a can be supplied with the maximum possible supply voltage U _v,max AsAnd (4) calculating.

But ohmic resistance R of the thermoelectric module _CU Are not generally known and are furthermore temperature dependent. To determine ohmic resistance R _CU Determined by experimentation with empirical relationships:

from this relationship, the actual temperature T of the thermoelectric module can be calculated _ist Ohmic resistance R in (simple to measure) _CU . Wherein R is _CU20 And R _CU150 Are empirical constants that give the ohmic resistance R of the thermoelectric module at 20 ℃ and 150 DEG C _CU 。

With full use of the heat available in the buffer store 21, the regulating variableThe regulating part R of the quantity Y serves for highly dynamic and precise regulation of the output temperature T _a (or another temperature as previously described). After the required power P for temperature regulation has been roughly adjusted by means of the model part A _V To reach the theoretical temperature T _soll The regulating part R then only has to correct the regulating variable Y by a small amount in order to achieve the desired precise regulating characteristic.

As mentioned above, in the adjusting unit 3 according to the invention, the heat flow between the substrate 20 and the buffer reservoir 21Plays a decisive role. In order to take account of this heat flow during regulationThe control error F is not linearly, but exponentially, included in the control component R, i.e. R = F (e) ^F ). The reason for this is the solution of the thermal power equation, which also contains an exponential component. The regulating deviation F is the theoretical temperature T in the design of the invention _soll And the actual temperature T _ist The difference between them.

It is noteworthy here that the theoretical temperature T _soll And the actual temperature T _ist Are related to the temperature to be regulated, i.e. for example the output temperature T _a Temperature T after the regulating unit 3 ₁ Reduced pressure temperature T _red Or the temperature T in the consumption sensor 5 _s . It is entirely possible, however, that the theoretical temperature T _soll And the actual temperature T _ist Different temperatures are involved in the model part A and the control part R, i.e. for example the temperature T in the consumption sensor 5 _s In the model part A, the temperature T is output _a In the regulatory moiety R.

For the regulating portion R, the regulating portion R is formed by a proportional portion Y _P And an integration part Y _I PI regulator of structure, i.e., R = Y _P + YI to select the classical way of regulating technical aspects. Hereinafter, the regulating portion R or the proportional portion Y is described _P And an integration part Y _I Possible specific design of (2).

Common proportional regulators are composed of a boost factor K _P Formed by weighting the adjustment error F by the enhancement factor, i.e. K _P F. Common integral regulators are composed of a boost factor K _I Formed by weighting the regulation error F according to the time t, i.e. K _I F.t, wherein the enhancement factor K _I As the adjustment time T _n The reciprocal of (c).

In the proportional part Y of the regulator according to the invention _P And an integration part Y _I In (1), the regulation error F is recorded as an exponential function F of the regulation error F _P (e ^F ) Or f _I (e ^F ). Thus, the proportional part Y _P In the simplest case Y _P ＝K _P ·f _P (e ^F ) And integrating part Y _I In the simplest case Y _I ＝K _I ·f _I (e ^F ). For a discrete-time regulator with a sample time Δ t (e.g., 10 milliseconds), the integral regulator may also be Y _I (n)＝Υ _I (n-1)+ΔΥ _I Form of (a), wherein, Δ γ _I ＝K _I ·f _I (e ^F ) Δ t. By applying an exponential function of the regulation error F, the heat propagation in the regulating unit 3 is approached.

As mentioned above, the energy fed into the conditioning unit 3 is used on the one hand to heat the gaseous medium and on the other hand also to heat the entire conditioning unit 3. At the same energy input, the temperature of the gaseous medium thus rises more slowly than the temperature of the gaseous medium decreases. As described above, the temperature increase is supported by the heat stored in the buffer store 21, so that this effect is already impaired thereby.

To compensate for this asymmetrical characteristic of the adjustment unit 3, the proportional part Y _P And an integration part Y _I Also using a suitable correction function Y _PowerCor Corrected, this results in a corrected proportional part Y _pCOr And a corrected integration part Y _ICor ：

Where H (x) is a known Heavisside function that depicts the true number as a quantity {0,1}, where x is&0 is H (x) =0, x&0H (x) =1, i.e. by correction, when the temperature of the gaseous medium should be increased, i.e. when T _soll >T _ist While reinforcing the proportional part Y _P And an integration part Y _I . When the temperature of the gaseous medium should be lowered, i.e. when T _ist >T _soll While, the proportional part Y _P And an integration part Y _I Is attenuated. As a correction function Y _PowerCor The following can be adopted:

the function contains a model part a. Thus, the stronger the adjustment intervention, i.e. the larger the model part a, the stronger the correction. Correction function Y _PowerCor The design of (A) is premised on the fact that model part A is normalized to the range [0,1]]Or [ -1,1 [ ]]。

In a preferred design, the proportional part Y is derived from a relationship formulated as follows _P ：

Integral part Y _I Exponential function f in (1) _I (e ^F ) In the preferred design, this is obtained from the relationship formulated as follows:

it should be noted here that, for the sake of simplicity, the integration part Y is also present _I In the middle adoptsEnhancement factor K of regulator _P But this is of course not necessary. Alternatively, of course, the own boost factor K of the integral regulator can also be used _I 。

For the case of time dispersion, the integrating part Y _I And is described as Y _I (n)＝Υ _I (n-1)+ΔΥ _I Wherein Δ γ _I ＝K _I ·f _I (e ^F )·Δt。

Where H (x) is again a Heavisside function and sign is a sign function that depicts the true number as the quantity { -1,0,1}, where x is&(lt, 0, sign (x) = -1, x =0, sign (x) =0, x)&gt, 0, sign (x) =1. The parameter σ is defined asAnd p =0.318366. For the integral part Y _I Function f of _I (e ^F ) It is chosen to be stable over the entire range and to have an exponential curve. To make this possible, the function is split into two parts. Wherein the first part has a logarithmic curve in the case of large adjustment errors. And a second part thereof has an exponential curve with a smaller adjustment error F. The transition between the first and second portions is made at a point p where the slopes of the two portions are the same to arrive at a continuous function.

The manipulated variable Y determined by the controller is generated therefrom, i.e. Y = a + R = a + Y _P +Y _I . It is worth noting here that the proportional part Y is preferably, but not necessarily, adopted _P And an integration part Y _I . However, it is also possible to use only the proportional part Y _P Or integral part Y _I . In addition, the damping factor Y can also be taken into account in the control variable Y _Df . The attenuation factor Y _Df May include a first attenuation factor Y _Df1 (e.g. an empirical value) to avoid overheating of the adjustment unit 3.

In addition, the attenuation factor Y _Df May further comprise a second attenuation factor Y _Df2 By means of this second damping factor, the theoretical overshoot can also be damped, for example, as a function of a maximum valueThe subtraction principle. Then, the attenuation factor Y is obtained _Df I.e. Y _Df ＝Y _Df1 ·Y _Df2 The two attenuation factors are optional and can be used independently of each other. In the application of attenuation factor Y _Df Then, the calculated manipulated variable Y becomes:

Y＝(A+R)·Y _Df ＝(A+Y _P +Y _I )·Y _Df

by means of this regulator, in combination with a specially implemented regulating unit 3, the desired temperature can be regulated with high precision and a high temperature stability can be achieved, which in the case of dynamic flow rates of the medium is a prerequisite for an accurate determination of the consumption quantity (mass flow rate, volume flow rate).

It should be noted here that the foregoing adjustments are independent of the particular application. Although this regulation is described in connection with the measurement of the consumption of a gaseous medium, the regulating unit 3 can be regulated in the manner described quite generally and is therefore also suitable for other applications in which the temperature of a medium, in particular also a liquid medium, is to be regulated. This is also possible because it can be adjusted to an arbitrary temperature, i.e. the temperature T after the adjustment unit 3 ₁ 。

However, the regulator can also be used to regulate the output pressure p _a Or the input pressure p _e And also according to the flowTo track the theoretical temperature T _soll Or temperature profile. The output pressure p can also be simulated _a And flow rateFor example by means of corresponding characteristic curves. When the flow rate isDependent on the output pressure p _a Or the input pressure p _e The regulator may also regulate the desired flow via pressure regulationThis allows the regulator to simulate the original structure (as it is used in a vehicle) and also the driving operation by the vehicle.

It should also be noted here that an arbitrary temperature in the consumption amount measuring device 1, but a temperature other than the consumption amount measuring device 1 may also be used as the theoretical temperature T _soll . But preferably will output a temperature T _a As the theoretical temperature T _soll To be adjusted. It is likewise possible to measure the output pressure p in the consumption measuring device 1 _a Or it may be measured outside the consumption measuring device 1, for example close to the consumers 6.

The described regulation is adapted to regulation by exploitation of the temperature span, and also to regulation with a switch between heating and cooling. In the case of a thermoelectric module as temperature control unit 23, the polarity of the supply voltage is reversed when the manipulated variable Y changes its sign. The adjustment variable Y is preferably normalized to the region [ -1,1] as described above.

In the case of hydrogen as the gaseous medium, heating can be caused by the pressure reduction in the pressure regulating unit 4. In this case, the key to whether cooling or heating is performed by the adjustment unit 3 is the input temperature T _e . The same applies substantially to liquid media.

To support the cooling, an additional cooling device 26, for example in the form of a cooling line 27 through which a cooling medium flows, may also be provided in the buffer reservoir 21 of the adjustment unit 3. The regulation can then be extended to regulate the cooling device 26, by means of which the active cooling by the cooling device 26 is taken into account. By varying the flow of cooling medium, for example(e.g. via a regulating valve or via pressure) and/or temperature T _K This adjustment may adjust the cooling device 26. For this purpose, an actuating variable Y is determined during the adjustment _C By means of which the cooling device 26 can be controlled.

The regulation of the active cooling should preferably have certain properties. The active cooling by means of the cooling device 26 is to be subjected to a base load, while the temperature control unit 28 is used to adjust the disturbances highly dynamically. In this case, however, it is necessary to ensure that the temperature control unit 28 always carries a part of the cooling load, in order to avoid having to operate the temperature control unit 28 in the vicinity of the zero point, which would lead to a constant changeover between cooling and heating. In the case of a peltier element as the temperature control unit 28, this would mean a constant polarity reversal, which would also lead to permanent damage to the peltier element. In addition, the advantage of the buffer store for adjusting the adjusting unit 3 is lost due to the operation near zero. In particular, the regulation of the active cooling should also be decoupled as far as possible from the regulation of the regulating unit 3, in order not to adversely affect this regulation.

To meet these requirements, a regulator is designed with a temperature difference Δ Τ _K Is exponentially incorporated into the regulator. Adjusted temperature difference Δ Τ _K Defined here as the temperature T of the tempering unit 28 _TE The temperature (which can be measured), preferably at the buffer storage 21 side (heating surface 25) and the actual temperature T of the cooling medium _K The difference between them. In order to avoid operating the temperature control unit 28 near zero, a predefined dead zone T can also be defined _totb By means of which the temperature T of the temperature control unit 28 can be corrected _TE . Whereby the corrected temperature T of the tempering unit 28 _KH Becomes T _KH ＝T _TE –T _totb And a temperature difference Δ Τ _K Becomes Δ Τ _K ＝T _KH -T _K . This makes it possible to design a P regulator which determines the manipulated variable Y for the cooling device 26 as follows _cp ：

Where H is again the Heaviside function and Y is the regulated regulating variable from the regulation unit 3. K is _CP Is the enhancement factor of the P regulator.

In order to ensure decoupling between the adjustment of the adjustment unit 3 and the adjustment of the cooling device 26, the adjustment is performedThe reaction time during the throttling of the cooling device 26 should be slower than the reaction time during the adjustment of the adjustment unit 3. In order to give a defined delay time for the adjustment of the cooling device 26, a filter G is used. Filter G receives as input signal a manipulated variable Y for cooling device 26 _CP And calculating a filtered manipulated variable Y _CPF This manipulated variable is then used as the actual manipulated variable for the cooling device 26, i.e. Y _CPF ＝G(Y _CP )。

Various known filters G can be used for this. In this case, a gaussian filter known from image processing proves to be advantageous, since such a filter has no overshoot and maximum rise time in a known manner. In addition, frequencies which are all above the limiting frequency are thereby attenuated. Such gaussian filters have long been known and are therefore not explained further here. It is also known that the calculation based on gaussian filters is complex and computationally expensive, which is disadvantageous for the tuning application. However, various solutions are known from the prior art for this purpose in order to minimize the computation time. In this case, so-called discrete gaussian kernels or scanned gaussian kernels may be considered.

Embodiments with active cooling in the buffer store are primarily useful for liquid media, but also for gaseous media. A large control range, for example-40 to 150 ℃, can thereby be achieved for the control unit 3 by means of the peltier element as the temperature control unit 28. The regulating unit 3 can thereby bring the required power over the entire regulating range and nevertheless regulate the temperature highly dynamically and always very precisely.

A preferred embodiment of the consumption measuring device 1 for a gaseous medium is described with reference to fig. 5. With input pressure p _e Is taken from the medium supply 2 and fed to the consumption measuring device 1 via the feed line 14 and the feed connection 15. A gas filter 30 can also be arranged on the input side, either outside or inside the consumption measuring device 1. The gaseous medium is temperature-regulated in the regulating unit 3 and is reduced in pressure in the subsequent pressure regulating unit 4 to a desired reduced pressure p _red . The depressurized gaseous medium then flows through a consumption sensor 5, in which consumption (mass flow, volume flow) is measured in the consumption sensor 5. Downstream of the consumption sensor 5, a second pressure control unit 7 is arranged, by means of which a desired output pressure p can be set _a . The conditioned gaseous medium is taken off via the output connection 16 and fed, for example, to the consumer 6.

All the functions and components described below are controlled or controlled by a control unit 40, in which control unit 40 the control unit 10 is also implemented. The constructed sensor also provides its measurement values to the control unit. For the sake of clarity, the control lines and measuring lines required for this purpose are not shown in fig. 4.

As consumption sensor 5, two or more coriolis sensors 31,32 are provided in series with one another. The two coriolis sensors 31,32 have different measurement ranges. This makes it possible to switch on the coriolis sensors 31,32 to the optimum (in terms of measurement accuracy) for measurement according to the consumption. This takes place here via a bypass switching valve 33, which is arranged in a bypass line 34 around the second coriolis sensor 33. Here, the switching valve 33 is operated via pressurized air. In contrast, a pressurized air valve body 35 is provided, which is connected to an external pressurized air supply device via a pressurized air connection 36. Thereby, the second coriolis sensor 32 can be turned on or off by operating the bypass switching valve 33. If two coriolis sensors 31,32 are flowed through, the verification of the measurement results is allowed in different measurement ranges, which can be used for self-control.

Furthermore, an overflow line 37 is provided in the consumption measuring device 1, which overflow line is connected to an overflow connection 38. The overflow line 37 is connected in the consumption measuring device 1 via a pressure relief valve to a gas path for the gaseous medium. This protects the consumption measuring device 1 against incorrect overvoltages.

A zero point balance valve 39 is arranged downstream of the consumption sensor 5. The zero point of the consumption sensor 5 can thus be checked. For this purpose, the zero point compensation valve 39 is closed (in this case again controlled via compressed air) and the measured values of the consumption sensor 5 at zero volume flow are evaluated. If the measured value exceeds a certain limit value, an internal sensor compensation can be initiated to adjust the zero point. In this way, the zero point drift of the consumption sensor 5 can be eliminated.

In the consumption measuring device 1, an inert gas purging device 41 is additionally provided in this exemplary embodiment. For this purpose, an inert gas accumulator 42 is provided, which is connected via an inert gas switching valve 43 to the gas path of the gaseous medium through the consumption measuring device 1. The inert gas accumulator 42 may be filled via an inert gas connection 44. The inert gas (e.g. nitrogen) required for purging the consumption measuring device 1 can be fed directly via the inert gas connection 44.

In order to purge the consumption measuring device 1 with inert gas, the input-side shut-off valve 45 is closed and the output-side output switching valve 46 is switched to the overflow line 37. At the same time, the inert gas switching valve 43 is opened. The gaseous medium under pressure which remains in the consumption measuring device 1 can thus escape via the overflow line 37. If the pressure decreases sufficiently, the check valve 47 opens and the consumption measuring device 1 is purged with inert gas, either until the inert gas accumulator 42 is empty or for a certain period of time. After purging, the consumption measuring device 1 is filled with inert gas (with a preferably low overpressure) and the consumption measuring device 1 is in a reliable state. The inert gas purge increases the reliability of the consumption measuring device 1 and can be activated, for example, when the installation is switched off or in the event of an emergency stop.

Claims

1. A method for adjusting an adjusting unit (3) with a base body (20) and a buffer reservoir (21), wherein a medium is guided through the base body (20), and a temperature control unit (23) with a first heating surface (24) and a second heating surface (25) is arranged between the base body (20) and the buffer reservoir (21), and wherein a temperature span between the first heating surface (24) and the second heating surface (25) is adjusted by means of the temperature control unit (23), characterized in that,

adjusting the regulating unit (3) in order to maintain a predetermined target temperature (T) of the medium _soll ) Wherein a control variable (Y) for controlling the control unit (3) is composed of a model part (A) and a control part (R), the model part calculating the power (P) required in the control unit (3) for controlling the temperature of the medium _v ) The adjusting part corrects the power (P) calculated by the model part (A) _v ) Wherein the theoretical temperature (T) _soll ) And the actual temperature (T) _ist ) The formed control error (F) is exponentially included in the control part (R).

2. Method according to claim 1, characterized in that the model part (a) calculates the power (P) required for tempering according to a relation formulated as follows _v )：

Wherein, T _hot ＝T _soll +Δp _G ·μ _JT 。

3. Method according to claim 2, characterized in that the power loss (P) of the adaptation unit (3) is taken into account in the model part (A) _L )。

4. Method according to claim 1, characterized in that said regulation portion (R) is constituted by a proportional portion (Y) _P ) And/or an integration part (Y) _I ) Composition, wherein the regulation error (F) is an exponential function (F) of the regulation error (F) _P (e ^F ),f _I (e ^F ) Is counted in the proportional part (Y) _P ) And/or the integrating part (Y) _I ) In (1).

5. Method according to claim 4, characterized in that said proportional part (Y) _P ) By the enhancement factor (K) _P ) And an exponential function f _P (e ^F ) And (4) forming.

6. Method according to claim 5, characterized in that said proportional part (Y) _P ) Calculated from the relationship formulated as:

7. method according to claim 5 or 6, characterized in that said proportional part (Y) _P ) By means of a correction function (Y) _PowerCor ) To be corrected to a corrected proportional part (Y) _pCOr )。

8. Method according to claim 7, characterized in that the corrected proportional part (Y) _pCOr ) Calculated from the relationship formulated as:

9. method according to claim 4, characterized in that said integration part (Y) _I ) By the enhancement factor (K) _I ) And an exponential function f _I (e ^F ) And time (t).

10. Method according to claim 4, characterized in that said integration part (Y) _I ) For a time-discrete regulator with a sampling time (Δ t), the gain is determined by an enhancement factor (K) _I ) And an exponential function f _I (e ^F ) And a sampling time (Δ t).

11. A method as claimed in claim 9 or 10, characterized in that the integration part (Y) _I ) Said exponential function of f _I (e ^F ) Calculated from the relationship formulated as:

12. a method as claimed in any one of claims 9 to 11, characterized in that the integration part (Y) _I ) By means of a correction function (Y) _PowerCor ) To be corrected into a corrected integral part (Y) _ICOr )。

Method according to claim 12, characterized in that the corrected integration part (Y) _ICOr ) Calculated from the relationship formulated as:

13. method according to claim 1, characterized in that a damping factor (Y) is taken into account in the adjusting variable (Y) _DF )。

14. Method according to claim 1, characterized in that a cooling device (26) is arranged in the buffer store (21), by means of which cooling device (26) coolant is conducted through the buffer store (21), and by calculating a regulating variable (Y) _CP ) To regulate the temperature (T) of the cooling device (26), the temperature regulating unit (23) _TE ) And the actual temperature (T) of the cooling medium _K ) Temperature difference (Δ Τ) therebetween _K ) Taking into account said regulating variable (Y) _CP ) In (1).

15. Method according to claim 14, characterized in that the temperature (T) of the tempering unit (23) _TE ) From dead space (T) _totb ) To correct for.

16. Method according to claim 15, characterized in that the adjusting variable (Y) is calculated according to _CP )：

。

17. Method according to any of claims 14-16, characterized in that the calculated regulating variable (Y) is _CP ) Filtered, and the filtered adjusting variable (Y) _CP ) For regulating the cooling device (26).

18. The method according to claim 17, characterized in that the filtering is implemented with a gaussian filter (G).

19. Use of the method according to any one of claims 1 to 18 for measuring the consumption of a gaseous medium, wherein the gaseous medium flows through a consumption measuring device (1) along a gas path (17), the consumption is measured with a consumption sensor (5), and the gaseous medium is tempered with the adjusting unit (3) before the consumption sensor (5), and the gaseous medium between the adjusting unit (3) and the consumption sensor (5) is depressurized, and the adjusting unit (3) is adjusted according to the tempering method.

20. The method according to claim 19, characterized in that the pressure of the gaseous medium after the adjustment unit (3) is regulated via a pressure regulating unit (4, 7).

21. Consumption measuring device for measuring the consumption of a gaseous medium, comprising an input connection (15) and an output connection (16), wherein the gaseous medium is fed to the consumption measuring device (1) at the input connection, wherein the gaseous medium is supplied by the consumption measuring device (1) at the output connection, wherein a gas path (17) is provided between the input connection (15) and the output connection (16), a consumption sensor (5) is arranged in the gas path, and an adjusting unit (3) for tempering the gaseous medium is arranged in front of the consumption sensor (5), and the adjusting unit (3) and the output connection (16) are connected to a supply line for supplying gaseous medium to the supply line, and a temperature regulating unit (3) for regulating the temperature of the gaseous medium is arranged upstream of the consumption sensor (5)A pressure regulating unit (4) is arranged between the consumption sensors (5), in which the gaseous medium is depressurized, characterized in that the regulating unit (3) has a base body (20), in which a medium line (22) through which the gaseous medium flows is arranged, and a buffer reservoir (21), the buffer reservoir (21) being designed to store heat, wherein a temperature regulating unit (23) is arranged between the base body (20) and the buffer reservoir (21), and a regulating unit (10) is provided, which regulates the regulating unit (3) in order to maintain a predetermined target temperature (T) of the gaseous medium _soll )。

22. Consumption measuring device according to claim 21, characterized in that a cooling device (26) is arranged in the buffer storage (21).

23. Consumption measuring device according to claim 21 or 22, characterised in that a further pressure regulating unit (7) is arranged after the consumption sensor (5).

24. Consumption measuring device according to claim 21 or 22, characterized in that the consumption sensor (5) is constructed from a plurality of coriolis sensors (31, 32) with different measuring ranges.

25. Consumption measuring device according to claim 21 or 22, characterised in that a zero-point balancing valve (39) is arranged in the gas path (17) behind the consumption sensor (5), by means of which zero-point balancing valve the gas path (17) can be shut off.

26. Consumption measuring device according to claim 21 or 22, characterized in that an inert gas purging device (41) is provided in the consumption measuring device (1), by means of which inert gas purging device the gas path (17) can be purged with inert gas.

27. Consumption measuring device according to any of claims 21 to 26, characterized in that the adjustment according to any of claims 1-18 is implemented in the adjusting unit (10).